Valve control means for fluid pressure systems



1951 w. H. WORTHINGTON 2,579,134

VALVE CONTROL MEANS FOR FLUID PRESSURE SYSTEMS Filed March :51. 1948 2 SHEETS-SHEET 1 1951 w. H. WORTIHINQGTONY 2,579,134

VALVE CONTROL MEANS FOR FLUID PRESSURE SYSTEMS Filed March 31, 1948 2 Sl-IEETS-SHEET 2 pressure inlets therefor.

Patented Dec. 18, 1951 VALVE CONTROL MEANS FOR FLUID PRESSURE SYSTEMS Wayne H. Worthington, Waterloo, Iowa, assignor to Deere Manufacturing (30., Dubuque, Iowa, a

corporation of Iowa Application March 31, 1948, Serial No. 18,198

This invention relates to a fluid pressure system and more particularly to a valve control means therefor.

The invention contemplates and has for its principal object the provision of means for automatically returning the control valve to neutral position in response to fluid pressure in excess of a predetermined value. The invention is particularly adapted for use in connection with hydraulic systems of the type used on agricultural tractors for raising and lowering or otherwise adjusting implements connected to the tractor. In systems of this type, it is common practice to provide valve control means operated by a pressure relief valve which functions in response to excess pressure to return the control valve to neutral so that the application of fluid pressure to the working cylinder or motor is discontinued. Itis the main object of the present invention to provide control means that is an improvement over existing systems and to provide such means in the form of a pair of relatively movable, axially shiftable pistons operably connected to the shiftable valve and deriving fluid pressure from a fluid pressure inlet under control of the excess pressure or relief valve. In some prior constructions in which fluid pressure means were used to operate directly on the control valve, it was necessary to provide a piston at each end of the valve and consequently to provide a pair of fluid In other types of systems, the pressure derived from the relief valve was used to operate mechanical linkage which in turn mechanically operated the means for controlling the valve. According to the present invention, the general organization is simplified by the use of piston means at one end only of the valve.

Another object of the invention is to provide improved relief valve means including primary and secondary relief valves for vthe purpose of diverting to the reservoir all fluid pressure in excess of that used to operate the means for returning the control valve to neutral. It is another object of the invention to provide simplifled control means for the valves, particularly an improved and simplified connection for bolding the valve in either of a pair of actuating or on positions, one of which may correspond to the functioning of the system in raising an implement, for example, and the other of which may correspond to the functioning of thesystem-in lowering such implement. I In the adjusting of agricultural implements mounted on or connected to tractors, it is desir- 5 Claims. (01.. 137-144) able that the fluid pressure system permit either fast or slow raising or lowering and for this purpose it has heretoforebeen known to provide a check valve of the poppet type incorporating therein a slidable valve of the piston type and to control this check valve so that. the initial movement of the control valve will open the piston valve to permitvrestricted exhaust of fluid pressure, the control valve being provided with means for ultimately opening the .valve to its fullest extent to provide for rapid. exhaust of fluid pressure. Another. object of the invention pertains to the provision of an improved valve construction of the type referred to, wherein the piston valve is interchangeable from end-to-end to provide aselection of means for metering or restricting the fluid pressure exhaust.

In connection withthe operation of a system by which the operator has-a choice of either fast or slow functioning, it is desirable that the means inludes some sort of mechanism which will indicate to the operator the position of the control valve in connection 'withthe change from slow operation to fast operation. In some known constructions, this device is incorporated in the control lever in the form of a cam element and detent meanswhich functions because of increased pressure on the detent to indicate to the operator to" change from slow phase to fast phase. According to the present invention, it "is an object to provide such means in connection with the piston means that functions to return the control valve to a neutral or to off position intermediate the two on positions. 7

The foregoing and other important and 'desirable objects and features inherent in and encompassed by the invention will become apparent to those skilled in the art as a disclosure is more fully made of a preferred form of the invention in the following detaileddescription and accompanyingsheets of drawings, in which Figure 1 is a sectional view of a control valve assembly, with diagrammatic illustrations of a pump and fluid motor associated with this assembly;

Figure 2 is a fragmentary transverse section taken on the line 2-2 of Figure 1 and illustrating the relationship between parts of the control system assembly; v

Figure 3 is a fragmentary view of the portion of the structure shown in Figure 1, with the parts illustrated in the positions they will occupy when the control valve is shifted upwardly;

-Figure 4 is a similar viewshowing the position of the parts when the control valve is shifted downwardly;

Figure is an enlarged transverse sectional view showing the check valve and metering valve assembly as constructed at one end thereof, the view being taken on the line 55 of Figure 1;

Figure 6 is a similar sectional view taken at the other end of the check valve assembly, as viewed along the line 6--5 of Figure 1; and

Figure '7 is a fragmentary transverse sectional view taken on the line 'Il of Figure l and illustrating part of the detent control mechanism for the control valve.

The invention is disclosed herein primarily as an adaptation thereof for the purpose of improving the construction disclosed and claimed in assignees co-pending application, Serial No. 626,626, filed November 5, 1945 by Jirsa et al., which issued on December 5, 1950 as Patent No. 2,532,552. It will be understood, of course, that the invention in its broader aspects may be adapted to other systems. Therefore, the illustration should be taken as an example of one application of the invention, and not as excluding other and modified forms thereof.

In the drawings, the numeral I0 designates a control valve housing provided with a vertical valve bore I2. The .housingis provided substantially centrally thereof with a fluid pressure inlet I4 by means of which fluid may be supplied, as by a pump IE, to an annular port I8 in communication with the bore I2. The bore I2 communicates adjacent its upper end with an enlarged annular low pressure or exhaust port which is in communication (by means not shown) with a fluid reservoir 22 preferably formed as part of the housing 18. A lower portion of the valve bore I2 is similarly in communication with a second low pressure or exhaust port 24, which likewise is in communication with the reservoir 22.

The housing I0 is provided with upper and lower annular discharge ports 26 and 28, respectively, these being in communication with the valve bore I2 above and below the inlet port I8. The valve bore I2 opens upwardly and outwardly at 38 at an upper portion of the housing and at a lower portion of the housing extends into an enlarged counterbore 32 which is closed at the bottom of the housing by a screwthreaded plug 34.

The housing carries for vertical reciprocation in the valve bore I2 a main or control valve, indicated generally by the numeral 36. This valve includes a central substantially cylindrical portion 38, an upper integral cylindrical or spool portion 40, and a similar lower spool portion 42. In the central or off position of the valve 36, the portion 38 is within the inlet port I8 and the spool portions 40 and 42 are respectively within the exhaust ports 20 and 24. The upper portion of the valve 36 is provided with an integral axial extension 44 which is notched at 46 to provide a gear-tooth connection with a control arm '48 fast on a transverse rockshaft 58. The rockshaft 59 may be rocked in either direction by a control lever 52 for moving the valve 3'6 either upwardly or downwardly at the will of the operator. The rockshaft 50 has also secured thereto a generally triangular cam plate 54 which has a central notch 56 normally engaged by the edge of a detent plunger 58. This plunger is carried in a housing portion 60 by means of a vertical bore 62, yie'ldable means in the form of a compression spring 64, and a guiding sleeve 66 carried in the bore 62. The detent head is provided with a slot 68 within which the lower edge of the cam plate 54 is received. This construction. provides at each side of the 0am plate a projection "I8 which confines the cam plate against tipping laterally with respect to the detent. Since the cam plate is secured to the rockshaft 50, the construction also prevents shifting of the rockshaft along its axis, The slotted portion of the detent head between the projection 10 is arcuate, as at 12, to fit the notch 56 in the bottom of the plate 54.

The plate is further provided with a pair of lower end portions 14 and "I6, each of which is preferably formed on an arc having the same radius as the arc I2. When the control lever 52 is moved to rock the rockshaft 50 in a countercl-ockwise direction, as viewed in Figure l, the end portion I4 will engage the detent head 58; conversely, when the rockshaft is rocked in the other direction the end portion 18 will engage the detent head. In view of the straight or flat surface between the detent portions 74 and I6, there will be intermediate positions of the control or rockshaft 58 in which the detent will not positively hold the cam plate 54. In other words. the operator may move the control lever 52 to .a limited extent in either direction without positively locking the lever in any definite position. Thereupon, the operator may release the lever 52 and the spring loading of the detent will tend to return the control lever to the position shown in Figure 1. The general functioning of the mechanism in this respect is similar to, that obtainable in the structure disclosed in the copending application referred to above and is provided for the purpose of increasing the sensitivity of the control. However, when the control lever 52 is moved to either of its maximum positions, it will'remain there until released either by the operator or by the return mechanism to be set forth below.

That portion of the valve 36 intermediate the cylindrical portion 38 and spool 40 is reduced in diameter at 18 and is tapered at 80,.and these portions are ground off to provide a flat 82. The fiat 82 is of sufficient length so as to be always in communication with the upper annular'port 26, and the lower end of the fiat is formed as an arc 84. The valve 36 is similarly formed between the portion 38 and the portion 42 with a reduced portion 85, a tapered portion 88, and a .fiat 90, the latter joining the intermediate portion 38 in an arc 92.

The upper annular port 25. communicates via a passage 94 with a check valve port 96. The latter is in communication with a reduced counterbore 98 opening to the vertical control valve bore I-2 in the vicinity of the upper tapered valve portion 80. This portion of the valve is provided with a longitudinally running slot IIlIl that engages a ball I02 carried in the inner end of the counterbore 98. A hollow check valve I04 of the poppet type is slidably carried in the counterbore 98 and normally closes the port 96 off from a coaxial chamber I86. This chamber is internally formed with an annular groove I88 into which is snapped the outermost coil of a coil spring I II] to provide means against which the spring may react to hold a ball II2 against the head of the check valve I04.

The lower annular discharge port '28 is associated with structure that is symmetrical with that just described. The port is in communication with a check valve port II4 by means of a numeral I52.

passage H6. .The check valve port-H4 is provided with a counterbcreI I8 in which is slidably carried a check valve I20 of the poppettype, for normally closing the check valve port ofi from a chamber I22 in which is provided a spring and ball assembly I23-I24 .similar to thatdescribed in connection with the check valve I04. Thebore II8 opens to the valve bore I2 in the vicinity of the tapered portion 88 of the valve men'iber36. This portion of the valve member is provided with a longitudinally running slot or groove I216 which receives or engages a ball. I28 positioned in the inner end of the bore I I8. The check valve I20 is hollow and carries slidably thereina metering valve I30 which has inner and outer endportions I32 and I34. As best shownin Figure 5, the

inner end portion I32 isground oil at each-side at I36 to provide a pair of diametrically opposite flats. As best shown in Figure 6, the outer end I34 is ground ofi at only one side to provide a flat I38. The outer end portion of the check valve I20, just inwardly of its enlarged head, is provided with a plurality of radial bores or ports I40, certain of which may be communicated'with the flat I38. The metering valve I30 may bechanged end for end to dispose the'inner end portion I32 at the outer end portion of the check valve so that the flats I36 provide means for "communication between the port I40 and the check'valve'port I I4. Regardless of which end of the metering valve is disposed outwardly, the opposite'end is'normally engaged by the ball I28; and the outer' end engages the ball- I23 of the spring and ball" assembly I23- I24, the head of the check valve being conically recessed at I42 to receive the ball? The ball I23 thus serves as means to seal the'interior of the check valve I20 against communication between the valve port I I4 and discharge'chamber I22.

The construction of the other check valve I04 is similar to that just described and the inwardly projecting end of the metering valve shown at I44 as engaging the ball I02. Radial ports in the check valve I04 are indicated at I46. I

The discharge-chambers I06 and I22 are appropriately closed by plugs I48 and I50; respectively, but the chambers are in'com'm'unication with a fluid motor, indicated generally by the This motor is preferably of the two-way type and'includes a cylinder, 154 and a movable piston I56. The chamber I06 is communicated with one end of the 'cylinderI54 as by a fluid line I58. The'other' chamber I22 isconnected by a line I60 to the other end of the cylinder.

From the description thus far it will be seen that the control valve 36 may be shifted in either 'direction from a central oil position to either of a pair of on positions by means of the control lever 52 and rockshaft 50. Assuming that it is desired to operate the fluid motor I52 so that the piston I56 moves from right to left,-;as viewed in Figure 1, the control lever 52 will be rocked in a clockwise direction, resulting in downward shifting of the valve member 36. Assuming further that the control lever .52 is shifted to an extent less than that required to lock the cam plate 54 at point 16 with the detent 58, slow travel of the piston I56 from right to left' -will be obtained. When the control valve .36 is in its neutral or ofi" position, as shown "in Figure l, fluid entering-the high pressure port I4 enters the annular port I8 and escapes both upwardly and downwardly along theflats 82 and 90. Neither of the spool portions 40 or 42 closes off its associated exhaust port 20 or'24; consequently, the fluid is free to circulate back to the reservoir 22 at no appreciable pressure. Initial downward movement of the valve 36 results first in a closing 011 of the port 20 by the spool portion 40 of the valve, at I62; simultaneously, the. arc 920i the flat 90 moves past the lower edge of the annular port I8 and the cylindrical portion 38 cuts off the valve bore I2 at I64. Also simultaneously, the taper I 26 cams the ball I28 outwardly in the bore I I8 against the inner end of the metering valve I30, thus unseating the ball I23 from the seat I42 in the head of the check valve I20. Fluid exhausted from the left hand end of the cylinder I54 through the line I60 enters the chamber I22 and may pass by the metering flat I38 and through the ports I40 in the check' valve I20 into the check valve port II4, thence throughthe passage H6, 'into the port 28, along the flat 90 to the'port '24 and from there to the'reservoir '22. At the same time, the rise in pressure along the fiat 82 and through the port 26 and passage 94 forces the check valve I04 open against its spring IIO, whereupon fluid pressure is transmitted through the chamber I06 and through the line I58 to'the right hand end of the cylinder I54, thus moving the piston I56 from right to left.

Initial movement 'of' the valve 86 downwardly serves merely to 'open'the metering valve I30 in the check valve I20. Continued downward movement of the control valve 36 ultimately eflects opening of the check valve I20 itself, thus permitting the more rapid exhaust of fluid pressure from the fluid motor I52, giving to the operator a fast'exhaust as compared with a relatively slow exhaust obtainable upon initial movement of the valve 36;

Reversal of the operation of the fluid motor I52 may be obtained by rocking the control lever 52 in a counterclockwise direction, which moves the control valve 36 upwardly and effects exhaust of the fluid motor through the chamber I06, check valve port 66, passage 94 and port 26 to the reservoir 22. Fluid under pressure will be transmitted from the fluid pressure inlet I4, through the port I6, along the flat' 98, to

the passage I I6 and ultimately to the fluid motor the cylindrical portion '38 ultimately cuts offthe port I8 at I68.

As previously stated, the lower portion of the control valvebore I2 opens into a counterbore 32. The control valve 36 is provided with'mea'ns preferably in the for-in of an integral axial extension I10, of reduced diameter with respect to the bottom end of the spool portion 42. --The extension I10 is still further reduced to provide an integral extending rod portion I12 and is further enlarged intermediate its ends to provide ahead I14. The head I14 is slotted or notched in arr-axial direction at I16. The shoulder'formed at the junction between the bottom face of the spool portion 42 and the extension I10 provides a piston, designated by the numeral I18.- The-extension I10 carries a second piston I preferably'in the form of a centrally bored cup slidably carried on the rod portion I12. The inside diameter of the cup is such as to slidably fit the head I 14 and the outside diameter thereof is such as to slidably fit the counterbore The connection between the piston .I18 and be-of any conventional construction and is shown The resilient meansthus' provides mechanism for empires I is of the one-way type so that theymay move together in one direction and may have limited relative movement in eitherdirection. Movement of the piston I80 toward therzpiston .118 is stopped by the head I14, which-contacts the face of the cup member I80. Movement of the member I80 away from the piston H0 is stopped by a snap ring I02 carried bythe rod I12. Downward movement of thepiston i-iiflis further controlled or stopped .by a stop or snapring I84 carried by the housing coaxial with the counterbore 32.- A second and similarsnap ring I85 is carried by'the counterboreportion of the housing in. axially spaced relation to the snap ring. I84. The lowermost endof the rod I12 is fitted with a second stop or snap ring I103 which may be similarv to the small snap ring I82 previously described. Resilient mechanism is interposed betweenthe stop rings I82 and I88 and preferably comprises an upper washer I90, a lower Washer I92 and a. coiled compression spring I94.

.As' best shown in Figure 3., when the. control valve 35. is moved upwardly, the piston J80 moves with it, the piston being stopped at 13.6 by means of the annular shoulder formed in the valve bore I2 and the counterbore .32., The piston I80 is carried with the valve 30 by means of .the snap ring I82 on the rod I12... At the same time, the upper washer I90 engages the upper large snap ringJM, .thus eifecting contpression .of the coil spring 194 between the upper washer I90 and the lower washer I92.

When the control lever 52 is rocked ina clockwise direction to move the valve member 36 downwardly, the parts start out from the position shown in Figure 1 and end up in. the posi* tion shown in Figure 4. Initial downward movement of the valve member 36 causes axial downward movement, of course, of the extension 110, which movement is relative to the piston I80, since. the latter is at its lowermost position, as defined by the upper stop or snap ring I84. .Before the head I14 is engaged and stopped against the interior or base of the cup piston I80, the lower washer I92 will have engaged the lower snap ring I86; and further movement downwardly of the valve member 35 will .efiect compression of the spring I94, final downward movement of the valve member 36 being determined by engagement of thelower end of the piston I80 with the upper snap ring I84; (Figure i).

The proximate portions of the valve bore I2 and counterbore 32 within which the pistons other structure to which it is attached. This 4 means preferably takes the form of a pair of angularly related .iluid passages or conduits 202 and 204, the former of whichmay communicate with the high pressure inletport I4 toprovide a by-pass passage and the latter of which may I communicate with the chamber 200 just referred to. The passage 202 is provided with a springloaded excess pressure relief valve designated generally by the numeral 206. This valve may here as a phmger zu having a central boreilll passage: 202'.and a 931L111 radial boresaifl-which may-be at times .placed incommunication'with-thetransverse passage 204'... The position of theplungershownin Figure l'is its normal-position. -The valve 206 constitutes a primary relief vaive. .in..-coniunction with which a secondaryflelief valve '2I4Ioperates. 'The secoridary. valve :may include. a spring loaded ball valve 216 whichnormally closes a shortpassage 21B inqcommunication-with the transverse passage 204.. .The normal position of the ball 2:I-B is maintained-by a relatively light, spring 220. The :passageiIB is thus normally closed off from a chamber 222 which may communicate as by a passage .224 with. the reservoir .22.: The arrangement is such that excess pressure developed in the system, efiect transmission of fluid under pressure .throughthepass-ages 202 and 204 to the'chamber 200. However, as will be hereinafter pointed out, the excess pressure resulting in opening ofthe primary relief vvalvefllfi further operates to open the secondary relief valve 214, so. that only part of the excess ressure is delivered to thechamber 200 and the remainder is returned through, the chamber 222 and passage 224 tothereservoir 22. 7

The portion of the piston I is notched .or ported at .225 to, communicate with the inner end oiythe passage '2 0 4 at such time as said piston is in its. upward position (Figur 3).

w The operation of the valve control system in generalhas been set forth above, particularly in connection with. the movement of .thepiston -I 56 in the cylinder ifid of the hydraulicmotor I52. Likewise, operation of the detent control means 44-16 hasv been set forth above, .as has been the interchangeability of the metering valve I30.

The operation of the means for returning :the control .valve to neutral operates as. follows. parts are in their nentralor foif position, thecontrol valve 3-0 is centered, as Figure Both relief valves 20B and 2I4 are closed, and there is no circulation of fluid pressure. to the chamber .200. The piston I80 is in its lowermost or normal position, at its maximum distance tram the piston I18, as determined by the upper, large snap ring I84, which provides stop means-for the piston. When the control lever is :moved to its maximum position ,in a counterclockwise direction to raise the valve member and supply fluid under pressure to the left hand end of the/fluid motor I52, the snap ring I 82 on rod I12 engages the bottom of the piston I80 and moves or displaces this piston upwardly along with the valve .memherB-B and piston 118, so that the parts assume the positions show-n inF-igure 3', If the control member 5,2 is rocked only slightlycounterclockwise disection, the same rresul-t is obtained so iar as movement of the pistons. I18 and 1801s con oemed; however, the cam plate 54 approaches the posit-ion in which thegend 14 thereof is about to engage the edgeof. the detent 58, the upper washer. I80 of the resilient means will have engaged themnderside-of the snap ring iii-4, Further upwardmovement of the valve. 36 will be resisted by the spring a194,, the latter being compressed between the Washers I and I192. The operator will feel this increased resistance and will know that he has reached the end of slowphase operation and that if he moves the con-- trol lever 52 further in a counterclockwise direction, he will enter upon fast-phase operation.

indicating to the operator the transition between slow-phase and fast-phase operation. It will be appreciated that initial movement of the valve member 36 and piston I80 upwardly will cause a slight rise in pressure in the chamber 200. However, the spring 22!) on the secondary relief valve 2I4 is relatively light and will permit the ball 2I6 to become unseated from the end of the passage 2I8 to an extent sufficient to accommodate the increase in pressure.

When the valve 36 and pistons I18 and I80 are moved upwardly to their maximum position, as shown in Figure 3, fluid is being delivered through the passage II 6 and line I60 to the left hand end of the fluid motor I52, and the control lever will be maintained in its maximum position by means of the detent mechanism previously described. Now, when the piston I56 reaches the-right hand limit of its stroke, or when movement of the piston to the right is otherwise impeded, the pressure in the system will rise to an extent sufficient to open the relief valve 206, thus shifting the relief valve plunger 208 downwardly to align the ports 2I2 with the transverse passage 204, whereupon fluid pressure will flow into the transverse passage 204 and thence into the chamber 200. When the parts are in the position shown in Figure 3, fluid pressure enters from thepassage 264 into the chamber 200 by means of the port 226 in the piston I80. Since the area of the piston I18 is smaller than the total area presented to fluid pressure by the piston I60, the latter will move downwardly, carrying with it (because of the snap ring I82) the piston I18 and the entire valve assembly 36. The fluid pressure thus developed is suflicient to overcome the locking action of the detent mechanism, and, as the valve 36 moves downwardly, the control lever 52 is released and the parts returned to their off position, as shown in Figure 1. All fluid pressure in excess of that required to move the piston I60 downwardly is exhausted to the reservoir through the secondary relief valve 2I4. Return of the valve member 36 to its off position ultimately diverts fluid pressure back to the reservoir through the ports 26 and 24 and no further excess pressure will be developed or the relief valves 266 and 2 I4.

When the control lever 52 is rocked in a clockwise direction to only a limited extent, the operator has the same feel created by the resilient means, since the washer I92 engages the upper side of the lower snap ring I66 as the parts approach the positions of Figure 4. In this instance, the piston I80 remains in its starting position as determined by the upper snap ring I84. The valve 30 and piston I18 may move downwardly toward the piston I60 until the extreme lower end of the extension rod I12 strikes the inner end of the lower plug 34, which occurrence may be simultaneous with the engagement of 'the head I14 on the extension I with the interior or base of the cup shaped piston I80.

With the parts in their positions as indicated in Figure 4, the piston I56 will move from right to left in the cylinder I54. Upon the occasion of the piston I56 reaching the end of its stroke or being otherwise impeded in its travel, fluid pressure will rise and will be transmitted through the passages 262 and 264 to the chamber 260, in a manner similar to that previously described. Fluid pressure entering the chamber 206 will react against the now stationary piston I80 and Will force the valve 36 upwardly by pressure on the piston portion I18. The valve 36 will return to its neutral or off position and the fluid pressure will fall off, since the pump will then circulate fluid back to the reservoir through the ports 20 and 24 in the usual manner.

As previously stated, the foregoing relates to a preferred embodiment of the invention and only the most important objects and features of the invention have been set forth. It will be appreciated that other objects and features of the invention will suggest themselves to those skilled in the art, as likewise will several modifications and alterations in the preferred form illustrated, all of which may be accomplished without departing from the spirit and scope of the invention as set forth in the appended claims.

What is claimed is:

1. In a fluid pressure system having control valve mechanism shiftable from an intermediate neutral position to either of two actuating positions, said system further including a reliefvalve-controlled passage for by-passing excess fluid pressure, the improvement residing in means for automatically returning the control valve mechanism to neutral from either of its actuating positions in response to excess fluid pressure, comprising: housing means including a chamber provided with a first cylinder and a second larger cylinder and fluid conducting means therebetween; a piston reciprocable in the first cylinder in either direction away from an intermediate normal position; means connecting the piston to the control valve mechanism for reciprocation of the piston in either direction away from its normal position in accordance with shifting of said control valve mechanism; a piston in the second cylinder reciprocable therein between a normal position and a displaced position; means operably interconnecting the pistons including a one-way connecting device so constructed and arranged that movement of the first piston in one direction away from its normal position displaces the second piston and return of the second piston to its normal position returns the first piston to its normal position, and so that movement of the first piston in the opposite direction away from its normal position is relative to the second piston; and means including a fluid conduit connected to the aforesaid by-pass passage and to the chamber for supplying fluid pressure to the chamber between the pistons effective to move the pistons conjointly in one direction and relatively in the opposite direction, depending upon the positions of the pistons as determined by positioning of the control valve mechanism.

2. In a fluid pressure system having control Valve mechanism shiftable from an intermediate neutral position to either of two actuating positions, said system further including a reliefvalve-controlled passage for by-passing excess fluid pressure, the improvement residing in means for automatically returning the control valve mechanism to neutral from either of its actuating positions in response to excess fluid Pressure, comprising: housing means including a chamber provided with a first cylinder and a second larger cylinder disposed coaxially in end-to-end and fluid transfer relationship; a piston reciprocable in the first cylinder selectively toward or away from the second cylinder from an intermediate normal position; means connecting said piston to the control valve mechanism for such reciprocation in accordance with shifting of said control valve mechanism as aforesaid; a piston reciprocable in the second cylinder from a normal position to a displaced position toward the first cylinder; means cooperable between the second cylinder and second piston providing a stop fixing the limit of movement of said second piston away from the first cylinder; means extending axially between and operably interconnecting the pistons including a one-way connecting device so constructed and arranged that movement of the first piston from its normal position and away from the second cylinder will displace the second piston in the same direction and return of the second piston to its normal position will return the first piston to its normal position, and so that movement of the first piston from its normal position and toward the second cylinder and return will be relative to the second piston; and fluid-conducting means connected to the aforesaid by-pass passage and communicating with the chamber between the pistons for supplying fiuid pressure to move the second piston from displaced position to normal position and to react against the: stopped second piston in its normal position to move the first piston in the direction away from the second, cylinder and back to its normal position.

3. In a fluid pressure system having control valve mechanism shiftable from an intermediate neutral position to either of two actuating positions, said system further including a reliefvalve-controlled passage for by-passing excess fluid pressure, the improvement residing in means for automatically returning the control valve mechanism to neutral from either of its actuating positions in response to excess fluid pressure, comprising: housing means including a chamber provided with a first cylinder and a second larger cylinder disposed coaxially in end-to-end and fluid transfer relationship; a piston reciprocable in the first cylinder selectively toward or away from the second cylinder from an intermediate normal position; means connecting said piston to the control valve mechanism for such reciprocation in accordance with shifting of said control valve mechanism as aforesaid; a piston reciprocable in the second cylinder from a normal position to a displaced position toward the first cylinder; means cooperable between the second cylinder and second piston providing a stop fixing the limit of movement of said second piston away from the first cyiinder; means providing an aperture through the second piston; a rod secured to the first piston and extending axially and slidably through said aperture and axially beyond saidsecond'piston; means on the rod on a portion thereof axially beyond the second piston and engageable with said second piston to provide a one-way connection between the pistons so that movement of the first piston from its normal position and away from the second cylinder will displace the second piston in the samedirection and return of the second piston to its normal position will return the first piston to its normal position, and so that movement of the first piston from its normal position and toward the second cylinder return will be relative to the second piston; and fluid-conducting means connected to the aforesaid by-pass passage and communicating with the chamber between the pistons for supplying fluid pressure to move the second piston from displaced position to normal position and to react against the stopped second piston in its normal position to move the first piston in the. direction away from the second cylinder and back to its normal position.

i. In a fluid pressure system having a housing provided with a valve bore in which a valve plunger is shiftable from an intermediate neutral position to either of two actuating positions, said system also including a relief-valve-controlled passage for by-passing excess fluid pressure, the improvement-residing in means for automatically returning the valve plunger to neutral position fromeither of itsv actuating positions in response to excess fiuid pressure in the system, comprising: means including a coaxial continuation of said valve bore providing afirst cylinder; a second larger cylinder arranged coaxially of and in end-to-end relationship with the first cylinder,

the two cylinders thus being open to each other and providing a fluid chamber; means including an end portion of the valve plunger "providing a first piston reciprocable in the first cylinder from a. normal position, when the valve plunger is in neutral position, either toward or away from the second cylinder when said valve plunger is shifted respectively to its actuating positions; a piston reciprocable in the second cylinder from a normal position to a displaced position toward the first cylinder; means cooperable between the second cylinder and second piston providing a stop fixing the limit of movement of said second piston away from the firstcylinder; means extending axially between and operably interconnesting the pistons including a one-way connecting device so constructed and arranged that movement of the first piston from its normal position and away from the second cylinder will displace the second piston in the same direction and return of the second piston to its normal position will return the first piston to its normal position, and so that movement of the first piston from its normal position and toward the second cylinder and return will be relative to the second piston; and fluid-conducting means connected to the aforesaid by-pass passage and communicating with the chamber between the pistons for supplying fluid pressure to movethe second piston from displaced position to normal position and to react against the stopped second piston in its normal position'to move the first piston in the direction away from the second cylinder and back to its normal position.

5. In a fiuid pressure system having a housing provided with a valve bore in which a valve plunger is shiftable from an intermediate neutral position to either of two actuating positions, said system also including a relief-valve-controlled passage for by-passing'excess fluid pressure, the improvement residing in means for automatically returning the valve plunger to neutral position from either of its actuating positions in response to excess fiuid pressure in the system, comprising: means including a coaxial continuation of said valve bore providing a first cylinder; means including an end portion of the valve plunger providing a piston reciprocable in the first cylinder in either direction away from an intermediate normal position; means including a second,v larger cylinder proximate to the first; means interconnecting said cylinders in fluid transfer relationship so that said cylinders provide in effect a fluid chamber; a piston in the second cylinder reciprocable therein between a normal position and a displaced position; means operably interconnecting the pistons including a one-way connecting device so constructed and arranged that movement of the first piston in one direction away from its normal position displaces the second piston and return of the second piston to its normal position returns the first piston to its normal 13 14 position, and so that movement of the first piston REFERENCES CITED in the opposite direction away from its normal The following references are of record in the position is relative to the second piston; and file of this patent: means including a fluid conduit connected to the aforesaidby-pass passage and to the chamber 5 UNITED STATES PATENTS for supplying fluid pressure to the chamber be- Number Name Date tween the pistons effective to move the pistons 769,111 Pierce Aug. 30, 1904 conjointly in one direction and relatively in the 2,184,793 Clench Dec. 26, 1939 opposite direction, depending upon the positions 2,342,450 Campbell Feb. 22, 1944 of the pistons as determined by positioning of 10 2,355,758 Stevens Aug. 15, 1944 the control valve plunger. 2,387,007 Buchanan Oct. 16, 1945 2,403,519 Gardiner July 9, 1946 WAYNE H. WORTHINGTON- 2,451,730 Greenlee Oct. 19, 1948 

